DE102018124809A1 - Dual co-drive system for an electric machine with a selective amplifier of the electric machine - Google Patents

Abstract

A hybrid powertrain for a vehicle may include a co-drive manipulator having a first input configured to be driven by an internal combustion engine and a second input configured to be driven by a first electrical machine. The hybrid powertrain may also include a selective booster having first and second planetary gears, each of the first and second planetary gear sets having a rotating component mounted for rotation with a rotatable shaft driven by the co-drive manipulator a rotary input received at the second planetary gear set by a second electric machine selectively driving the output shaft at a plurality of gear ratios including at least one speed reducing gear ratio and a speed increasing gear ratio.

Description

INTRODUCTION

Hybrid propulsion vehicles typically use a combination of an internal combustion engine and at least one electric machine. The electric machine is typically a motor-generator, so that it can selectively supply the vehicle driveline with a rotational force to drive the vehicle or generate electrical energy for storage in a vehicle battery. The hybrid vehicle may supply the wheels using the electric machine, the internal combustion engine, or both.

Electric machines typically have a certain range of operating power in which they provide the greatest torque or power in proportion to the electrical power consumed. Larger ranges of operating power inevitably increase the complexity and / or cost of electrical machines. As a result, manufacturers typically must compromise on the design of the electric machine and lose the lower speed efficiency of the electric machine for higher efficiency at higher speeds of the electric machine, or vice versa. Hybrid vehicles therefore often employ electric machines with a limited speed range, e.g. B. only at speeds below a predetermined threshold.

Accordingly, there is a need for an improved hybrid powertrain that solves the aforementioned problems.

SUMMARY

In an exemplary illustration, a hybrid vehicle having an internal combustion engine and a plurality of electric machines is provided. The vehicle may also include a hybrid powertrain. In at least one example, the hybrid powertrain includes a co-drive manipulator and a selective amplifier for an electric machine. The co-drive manipulator may include a first input configured to be driven by an internal combustion engine and a second input configured to be driven by a first electrical machine. The hybrid powertrain may also include a selective amplifier having first and second planetary gear sets. The planetary gear sets may include a ring gear, a sun gear, and a plurality of planetary gears interposed therebetween which are held spaced from the sun gear by a rotatable planet gear carrier. Each of the first and second planetary gear sets may include a rotating component mounted on a rotatable shaft for rotation therewith such that a rotating input received at the second planetary gear set by a second electric machine selectively rotatably drives the rotatable shaft at a plurality of gear ratios which includes at least one speed reducing ratio (ie, a reduction or understeer gear) and a speed increasing ratio (ie, an overdrive gear).

Optionally, the hybrid powertrain may include a rotary clutch configured to selectively limit relative rotation between components of the first and second planetary gear sets, such as a first ring gear of the first planetary gear set and a second planet gear carrier of the second planetary gear set. The rotary clutch may also be configured to selectively limit the rotation of a second planetary gear carrier of the second planetary gear set with respect to a first ring gear of the first planetary gear set.

In some examples, the hybrid powertrain may also include a first brake clutch that is configured to selectively restrict rotation of the first ring gear. In at least some examples, the brake clutch is configured to limit rotation of a sun gear of the first planetary gear set and a planet gear carrier of the second planetary gear set. A second brake clutch may be provided in at least one exemplary approach, wherein the second brake clutch is configured to selectively limit the rotation of the second planet carrier.

Optionally, an input brake clutch may be provided for selectively limiting the rotation of the first input, e.g. B. from the internal combustion engine is designed.

In at least some approaches, components of the planetary gear sets may be interconnected for synchronous rotation. For example, the second planet carrier may be connected to a first sun gear of the first planetary gear set for rotation therewith. Likewise, the first planetary gear set may include a first sun gear fixed to a second planet carrier of the second planetary gear set for rotation therewith.

Optionally, the co-drive manipulator includes a third planetary gear set (in addition to those of the selective amplifier). In these examples, the first input may be a planet carrier of the third planetary gear set, the second input may be a sun gear of the third planetary gear set, and / or the rotatable shaft may be of a type Ring gear of the third planetary gear set to be driven.

The rotatable shaft may be coaxial with the co-drive manipulator and its rotating components arranged or offset, for. B. in a countershaft arrangement.

In some exemplary approaches, a selective amplifier for an electric machine in a hybrid powertrain includes first and second planetary gear sets. The first planetary gearset may include a first ring gear, a first planet carrier, and a first sun gear, the first planet carrier mounted on a rotatable shaft for rotation therewith. The second planetary gear set may include a second ring gear configured to receive an input from an electric machine, a second planet gear carrier attached to the first sun gear for rotation therewith and a second sun gear mounted to the rotatable shaft for rotation therewith is attached. The first and second planetary gear sets may cooperate to provide a plurality of ratios between the second ring gear and the rotatable shaft, including at least one speed reducing gear ratio and a speed increasing gear ratio.

In at least some examples, a selective amplifier for an electric machine includes a rotary clutch configured to selectively fasten rotating components of the first and second planetary gear sets for rotation therewith, e.g. B. the first ring gear of the first planetary gear set on the second planet carrier of the second planetary gear set to create a uniform transmission ratio. The selective amplifier may also include a first brake clutch configured to selectively limit rotation of the first ring gear relative to a stationary housing and a second brake clutch configured to selectively limit rotation of the second planet carrier relative to the stationary housing ,

list of figures

• 1A ist ein schematisches Diagramm, das eine Ausführungsform eines Antriebsstrangs in einer Querschnittsansicht, z. B. für ein Hybridfahrzeug, unter Verwendung einer koaxialen Konfiguration darstellt;
• 1B ist ein schematisches Diagramm, das eine Ausführungsform eines Antriebsstrangs in einer Querschnittsansicht, z. B. für ein Hybridfahrzeug, unter Verwendung einer Vorgelegewellenkonfiguration darstellt;
• 1C ist ein Hebeldiagramm, das die Antriebsstränge aus den 1A und 1B darstellt;
• 2 ist ein Hebeldiagramm, das einen selektiven Verstärker für die Antriebsstränge aus den 1A-1C darstellt; und
• 3 ist ein Hebeldiagramm, das die Antriebsstränge aus den 1A-1C darstellt und exemplarische Verbindungen mit einem Verbrennungsmotor und zwei elektrischen Maschinen darstellt.

One or more embodiments of the invention will be described hereinafter in conjunction with the accompanying drawings, in which like designations denote like elements, and in which:

• 1A is a schematic diagram illustrating an embodiment of a drive train in a cross-sectional view, for. For a hybrid vehicle, using a coaxial configuration;
• 1B is a schematic diagram illustrating an embodiment of a drive train in a cross-sectional view, for. For a hybrid vehicle, using a countershaft configuration;
• 1C is a lever diagram that shows the drive trains out of the 1A and 1B represents;
• 2 is a lever diagram showing a selective amplifier for the drive trains from the 1A-1C represents; and
• 3 is a lever diagram that shows the drive trains out of the 1A-1C represents and exemplifies connections with an internal combustion engine and two electric machines.

DETAILED DESCRIPTION

Exemplary representations of a hybrid powertrain for a vehicle utilizing an internal combustion engine and at least one electric motor generator or electric machine are provided. The exemplary illustrations may allow for optimal use of multiple electric machines in a hybrid mode, i. H. when the internal combustion engine and one or more electric machines are used for powering the vehicle wheels, and in an electric vehicle mode in which only the electric machine (s) are used for power supply.

In one example, the optimal use of two electric machines that are co-powered (ie, each electric machine powers the vehicle wheels) in both hybrid mode and EV mode is through a selective primary electric machine prime mover allows. In particular, the selective amplifier can be used to limit the use of the primary electric machine in a relatively low speed range (when the primary electric machine is used as a torque controller with understeer) and a relatively fast speed range (when the primary electric machine is used as an overdrive speed amplifier ) to facilitate. In addition, a co-drive hybrid system, i. H. when using multiple electric machines, advantageously allow the use of relatively smaller electric machines instead of a single electric machine. That is, hybrid systems that use a single electric machine generally require a much larger electric machine.

Exemplary representations of a hybrid powertrain, for example, two brake clutches, z. B. as components of the selective Amplifier, use to manipulate the performance of a primary of the electric machines for a low or a high speed range. In addition, a rotary clutch can be used to provide a unity drive (ie, a 1: 1 ratio) for the electric machine. In this way, a robust drive architecture is provided for both the hybrid and the electric mode, which allows for optimal utilization of the electric machine and power manipulation.

The exemplary powertrain architectures disclosed herein are generally compact and modular and may be implemented in a coaxial or countershaft arrangement. Accordingly, the exemplary powertrains disclosed herein may be implemented in transverse engine / transmission configurations (typical for front-wheel and electric four-wheel drive configurations) or in longitudinal engine transmission configurations (typical for rear-wheel and four-wheel drive configurations) and in any suitable vehicle size segment.

As further described below, exemplary vehicle powertrains may provide a drive force for an axle drive unit via a co-drive manipulator, such as a planetary gear set. The planetary gear set may include a sun gear, a plurality of planetary gears, a planet carrier that holds the planet gears in spaced relation about the sun gear, and a ring gear. The sun gear, the planet gears and the ring gear may have any size or number of gears, which is useful for the operation of the planetary gear set. (For example, the ring gear generally has a greater number of gears than the sun gear and individual planet gears, as will be discussed in more detail below.) In at least some examples, planetary gear sets together provide a plurality of gear ratios to an output, e.g. As the final drive unit or an intermediate shaft of the planetary gear sets, of at least one primary electric machine of the drive train ready. Planetary gear sets can indeed be a manual transmission for one of the electrical machines, eg. As a primary electric machine, provide, so that a plurality of gear ratios with at least one speed-reducing transmission ratio, d. H. an understeer gear, and a speed increasing gear ratio, d. H. an overdrive transmission is available between one of the electric machines and the output shaft (or, in the case of a countershaft configuration, the countershaft). The availability of both a lower and a higher gear ratio makes it possible to distribute the optimum operating speeds of the electric machine over a wider range of vehicle operating speeds. This flexibility can be further enhanced by providing a uniform gear ratio (i.e., 1: 1), thereby spreading a relatively narrow range of optimum electrical machine speeds for use over a wider range of vehicle speeds.

With view on 1A-1C are exemplary vehicle powertrains 100a . 100b (together 100 ). The vehicle drive trains 100 can be used in a hybrid vehicle and, as mentioned above, in a coaxial configuration, the example of which in FIG 1A or in an offset / countershaft configuration, the example of which is shown in FIG 1B is shown executed. In each of the in the 1A and 1B In the illustrated diagrams, rotating components are generally illustrated in the section. A lever diagram applicable to each configuration is in 1C and will be used in conjunction with the following description of the operation of the exemplary powertrains.

In each of the 1A-1C sees a vehicle drive train 100 Power for a vehicle final drive 130 which, in a variety of modes, which will be described in more detail, an internal combustion engine 102 , a first electric machine 104 and a second electric machine 106 used. The illustrated internal combustion engine 102 is a gasoline / spark ignition engine, but it should be noted that there is generally no limitation on the type of internal combustion engine used. Only as an example, the internal combustion engine 102 be a diesel / compression ignition engine. The electrical machines 104 . 106 can each be motor generators. That is, the electric machines 104 . 106 each one may be capable of using the final drive 130 to selectively provide drive power to the vehicle wheels. When the electric machines 104 . 106 the final drive 130 Do not supply drive power, they can generate from the movement of the drive train electrical energy in one or more vehicle batteries (not shown) in electrical connection with the electrical machines 104 . 106 can be stored.

As in each of the 1A-1C represented, transferred the engine 102 and the electrical machines 104 . 106 each over a plurality of planetary gear sets 114 . 116 and 118 selectively a movement on the final drive 130 , The electrical machines 104 . 106 can also selectively generate electrical energy from the movement of the planetary gear sets 114 . 116 and 118 produce. For this purpose, the electrical machines 104 . 106 one stator each 104a . 106a and a rotor 104b . 106b include. The rotor 104b can rotate around an axis passing through the shaft 120 is set while the rotor 106b can rotate around an axis through a rotatable shaft 122 is fixed (or, in the case of the example in 1B to the countershaft 122 ' , as described in more detail below), the planetary gear sets 116 . 118 assigned. Rotating components of the planetary gear sets described below 114 . 116 and 118 In general, they can also rotate around an axis through the waves 120 . 122 or 122 ' is determined, as is apparent from the illustrations and the following description.

The planetary gear sets 114 . 116 and 118 may be of any configuration and generally operated according to the planetary or planetary gear principle, that is, when the rotation of various components thereof is used to provide different input / output ratios. The planetary gear sets 114 . 116 and 118 each generally include a sun gear 114 . 116 and 118 which are generally centrally located within the planetary gear sets 114 . 116 and 118 are arranged and define a plurality of outwardly extending teeth (not shown). The planetary gear sets 114 . 116 and 118 can also be a ring gear 114r . 116r and 118r include that of its respective sun gears 114s . 116s and 118s is arranged radially outward and defines a plurality of radially inwardly extending teeth (not shown). Furthermore, the planetary gear sets 114 . 116 and 118 each a plurality of planetary gears 114p / 116p / 118p include, with each variety of planetary gears 114p / 116p / 118p radially between the respective ring gear 114r / 116r / 118r and the sun wheel 114s / 116s / 118s is arranged. The planetary gears can each set a plurality of gears (not shown) with those of their adjacent ring gear 114r / 116r / 118r and the sun wheel 114s / 116s / 118s interlocked. Each of the planetary gear sets also includes a planet carrier 114c . 116c and 118c , the planet wheels 114p / 116p / 118p in a spaced relationship to the sun gears 114s . 116s and 118s stops and synchronizes with the centers of planetary gears 114p / 116p / 118p is turned.

Referring now to the 1A and 1C can the powertrain 100 as generally a co-drive manipulator 108 and a selective amplifier 110 are comprehensively considered, each of which cooperates to move to the final drive 130 to transfer (and, in the case of electrical machines 104 . 106 to make a rotary motion to the electric machines 104 . 106 to provide electrical energy). In particular, the co-drive manipulator 108 and the selective amplifier 110 each connected to a rotatable shaft, z. B. with an output shaft 122 (as in 1A) or a countershaft 122 ' (as in 1B) ,

As in the 1A and 1C illustrated is the powertrain 100a a coaxial arrangement in which the output shaft 122 parallel to a rotating shaft 120 of the manipulator 108 is aligned. The co-drive manipulator 108 has a first input for driving through the engine 102 in the form of the planet carrier 114c of the planetary gear set 114 is designed. A second entrance, in the form of the sun wheel 114s of the planetary gear set 114 , is for turning with the electric machine 104 connected. The ring gear 114r turn is on the shaft 122 and the planet carrier 116c of the planetary gear set 116 attached. Alternatively, in the in 1B Illustrated countershaft configuration illustrated the shaft 120 opposite the rotatable shaft 122 ' of the selective amplifier 110 offset, as will be explained in more detail below.

As in the 1A and 1B Best seen is the selective amplifier 110 the two planetary gear sets 116 . 118 Each of which interacts with the final drive unit 130 over the electric machine 106 to set in motion. When the electric machine 106 the final drive unit 130 not actively moving, it can also be in response to the planetary gear sets 116 . 118 received rotary inputs generate electrical energy. Each of the planetary gear sets 116 . 118 has a rotating component attached to the shaft 122 is attached for rotation with the same. In particular, the planet carrier 116c of the planetary gear set 116 and the sun wheel 118s of the planetary gear set 118 each on the waves 122 or 122 ' attached for rotation with these.

The planetary gear sets 116 . 118 work together to create a variety of translations for the electric machine 106 to power the shaft 122 or 122 ' provide. In particular, the electric machine 106 directly or via an additional gear with the ring gear 118 coupled (in the 1A-1C not shown). Accordingly, the ring gear 118r of the planetary gear set 118 an input for the electric machine 106 to the shaft 122 or 122 ' (and ultimately the final drive unit 130 ) to put in a rotary motion. The ring gear 118r In addition, it selectively drives the wave 122 or 122 ' with a variety of translations, the at least one reduction ratio (ie when the shaft 122 / 122 ' slower than the ring gear 118r ) and an overdrive ratio (ie when the shaft 122 / 122 ' Turns faster than the ring gear 118r ) about the planetary gear sets 116 and 118 include, like will be described in more detail below. In addition, in some examples, in addition to the understeer and understeer conditions, a uniform oversteer condition may be provided (ie, when the shaft 122 / 122 ' rotating at the same speed as the ring gear 118r ). The planetary gear sets 116 . 118 moreover, offer the variety of gear ratios in a relatively compact and inexpensive arrangement.

The variety of the planetary gear sets 116 . 118 provided gears may be equipped with one or more clutches, the rotating components of the planetary gear sets 116 . 118 selectively secure for rotation with each other or the rotation of components of the planetary gear sets 116 . 118 selectively on a stationary housing 113 may be limited, as described in more detail below.

As in particular in the 1A and 1B can be seen, is the planet carrier 118c of the planetary gear set 118c on the sun wheels 116s of the planetary gear set 116 attached. In addition, both the planet carrier 116c of the planetary gear set 116 and the sun wheel 118s of the planetary gear set 118 on the shaft 122 or 122 ' attached for rotation with these.

In addition, limited a brake clutch 124 selectively the rotation of the ring gear 116r of the planetary gear set 116 in relation to a stationary housing 113 (or, in the example of 1B , the case 113b ) of the powertrain. A second brake clutch 126 is designed to the rotation of the planet carrier 118c in relation to the housing 113 / 113b selectively limit. As well as the planet carrier 118c at the sun wheel 116s attached to rotate with this, the brake can 126 also the rotation of the sun wheel 116s in relation to the housing 113 selectively limit. As described in more detail below, the brake clutches 124 . 126 selectively different effective gear ratios between an input of the electric machine 106 ie the ring gear 118r , and the wave 122 or 122 ' generate both an understeer ratio and an oversteer ratio.

As also illustrated, a rotary clutch 128 be designed, which is designed to rotate components of the planetary gear sets 116 . 118 to fix selectively for rotation with each other, that is, to rotate at the same speed. In some examples, mounting components of the planetary gear sets 116 . 118 a uniform translation for the electric machine 106 create, ie in relation to the wave 122 or 122 ' , For example, as in the 1A and 1C illustrates the rotary coupling 128 for selectively limiting the rotation of the planet carrier 118c of the planetary gear set 118c in relation to the ring gear 116r of the planetary gear set 116 designed. In addition, as will be described in more detail below, the rotary coupling 128 other rotating components of the planetary gear sets 116 . 118 connect to a single translation for the electric machine 106 to accomplish.

The powertrain 100 can also have an input brake clutch 112 include the rotation of the first input, ie the shaft 120 in relation to a stationary housing 113 (or, in the example of 1B , the case 113a ) selectively limited. Accordingly, the input brake clutch 112 with the engine off 102 be pressed to turn the shaft 120 and thus the planet carrier 114c of the planetary gear set 114 to prevent. The engagement of the input brake clutch 112 therefore, causes the planetary gear set 114 has only one degree of freedom (as opposed to two degrees of freedom when the input brake clutch 112 not actuated), causing the two electrical machines 104 . 106 independent of the engine 102 can be operated as a rotation of the shaft 120 is prevented. In addition, the input brake clutch 112 the noise, vibration and roughness characteristics of the powertrain 100 improve by otherwise rotating components, such. B. the shaft 120 , fixed holds.

Actuation of the brake coupling 124 (and releasing the brake clutch 126 ) may be a speed reducing or understeering ratio between the ring gear 118r and the wave 122 or 122 ' generate, which by the electric machine 106 output torque is increased and acts as a "torque amplifier". In particular, the brake clutch stops 124 the ring gear 116r in relation to the housing 113 in the stationary state. As a result, the electric machine turns 106 the ring gear 118r of the planetary gear set 118 , The ring gear 118r causes a rotation of the planet carrier 118c which also causes the sun gear 116s turns (that on the planet carrier 118c attached to rotate with it). Because the ring gear 116r remains stationary, causes the rotation of the sun gear 116s a rotation of the planet carrier 116c , The output shaft 122 rotates at the same speed as the planet carrier 116c , It should be noted that, since the sun wheel 118s and the planet carrier 116c for a synchronous rotation (over the shaft 122 or 122 ' ) are attached to each other, and the planet carrier 118c and the sun wheel 116s are also attached to each other for a synchronous rotation, the sun gears 116s . 118s one identical each Must have size / configuration. Furthermore, the planetary gears must 116p . 118p that the planetary carriers 116c . 118c are assigned, each having an identical size / configuration. Since the ring gear of a planetary gear generally has more and more teeth than the associated sun gear, each gear size / number of teeth of the relevant components of the planetary gear sets 116 . 118 when operating the brake coupling 124 to an understeer ratio.

Actuation of the brake coupling 126 (and releasing the brake clutch 124 ), in contrast, a speed-increasing or overdriving ratio between the ring gear 118r and the wave 122 or 122 ' create and thus the speed over that of the electric machine 106 increase, so that the selective amplifier, a "speed amplifier" for the electric machine 106 in terms of the wave 122 or 122 ' is. The brake coupling 126 holds the planet carrier 118c and the sun wheel 116s in the stationary state. As a result, the rotation of the ring gear causes 118r through the electric machine 106 a rotational movement of the sun gear 118s that on the shaft 122 or 122 ' is attached for rotation with this. As mentioned above, the ring gear of a planetary gear set generally has more and more teeth than the associated sun gear, and accordingly, any gear size / number of teeth will produce the relevant components of the planetary gear sets 116 . 118 when operating the brake coupling 126 an overdrive ratio.

In examples in which a rotary clutch 128 is provided, a uniform drive ratio by the joint fixing components of the planetary gear sets 116 . 118 (and the release of the brake couplings 124 and 126 ), z. B. the planet carrier 118c and the ring gear 116r , getting produced. In particular, the rotation of the ring gear causes 118r through the electric machine 106 a rotation of the ring gear 116r and the sun wheel 116s at the same speed. Accordingly, the planet carrier rotates 116c at the same speed and turns the shaft 122 or 122 ' also at the same speed. A uniform drive ratio may provide additional flexibility by providing another gear ratio between the understeer and oversteer ratios. By way of example only, uniform drive ratio may be useful in plug-in hybrid vehicles (which may have a relatively extended drive range in the pure electric mode, in part because of a relatively larger battery pack) and larger vehicles because of generally higher duty cycles for the electric machines.

As mentioned above, exemplary drive trains 100 in a coaxial or countershaft configuration. In particular, the effects in 1A illustrated powertrain 100a a rotational movement of the rotatable shaft 122 directly over the ring gear 114r that on the shaft 122 and the planet carrier 116c is attached for rotation with this. Accordingly, the wave 122 coaxial with the shaft 120 aligned. Such a coaxial configuration may be suitable only as an example of a rear-drive or four-wheel drive vehicle.

In other examples, however, a countershaft configuration may be used that can generally provide a more compact powertrain. Such as in 1B shown is the drive train 100b otherwise identical to the powertrain 100a , but uses a countershaft 122 ' concerning the wave 120 is offset to the power on an output shaft 140 to transmit (in contrast to the coaxial waves 120 and 122 ). For example, the ring gear 114r with a spur gear 111 be meshed, z. B. each have an external toothing (not shown). The gear 111 turn, is at the counter-wave 122 ' attached. The countershaft 122 ' has an additional spur gear at a distal end 134 on. The gear 134 in turn is with a spur gear 144 toothed, that on the output shaft 140 is attached. Accordingly, the countershaft can 122 ' each of the shaft 120 and / or the output shaft 140 associated fixed gear ratio drive or driven by this, which is suitable, for. B. the spur gears 111 respectively. 134 , Thus, the powertrain 100b functionally identical to the coaxial powertrain 100a because both are represented by the lever diagram, which refers to the respective 1C . 2 and 3 refers. (In 1C that's through the spur gears 111 . 134 provided fixed gear ratio in 1B not shown.) In the coaxial drive train 100a rotate rotating components of the electric machine 106 , the gears 111 and 134 and rotating components of the planetary gear sets 116 and 118 each about an axis, that of the rotating shaft 122 assigned. In contrast, turning in the countershaft drive train 100b the rotating components of the electric machine 106 , the spur wheels 111 and 134 and the rotating components of the planetary gear sets 116 and 118 each about an axis, that of the rotating countershaft 122 ' assigned.

The countershaft configuration of the powertrain 100b can offer a more compact design suitable for front-wheel drive or other applications where drivetrain space is very limited. A countershaft configuration may be for a number of reasons Reduction in the overall size of the powertrain 100b compared to a coaxial configuration, e.g. B. the drive train 100a , For example, the ring gear (ring gears) may be smaller in a countershaft configuration because an external fixed gear ratio can be used to provide any output speed, even with the smaller ring gear (s). B. via one or more spur gears, as described above. In addition, a countershaft and, in this case, all other input / output shafts thereof can be spatially positioned at different levels, which is the overall size of the powertrain 100b makes it even more compact. For example, in 1B the countershaft 122 ' , the output shaft 140 and the drive shaft 120 not coplanar with respect to each other (while in the two-dimensional 1B appear planar).

Referring now to 2 , which is a lever diagram of the selective amplifier 110 of the powertrain 100a or 100b equivalent to the lever diagram of 1C is, the operation of the selective amplifier 110 described in more detail. The planetary gear sets 116 . 118 actually form a manual transmission 132 that has a variety of translations for the electric machine 106 in terms of the wave 122 or 122 ' provides. In addition, as mentioned above, the shaft 122 or 122 ' also on the ring gear 114r of the planetary gear set 114 (not in 2 shown) for rotation with this attached. Accordingly, the power of the engine 102 and / or the electric machine 104 (each via the ring gear 114r the power on the shaft 122 or 122 ' transferred) with the electric machine 106 be combined.

As in 2 shown, the ring gear 116r when operating the brake coupling 124 secured against twisting and an understeer ratio of the input ring gear 118r to the wave 122 or 122 ' produced. In particular, the electric machine is turning 106 the ring gear 118r and thus the planet carrier 118c and the sun wheel 116s together with the same speed. The stationary ring gear 116r causes the planet carrier 116c in response to the rotation of the sun gear 116s turns and thus the shaft 122 or 122 ' rotates. In addition, the rotational speed of the shaft 122 or 122 ' less than that of the input ring gear 118r caused by the reduction of the angular velocity between the ring gear 118r and the rotating planet carrier 118c , It should be noted that the identical size / tooth configuration of the sun gears 116s . 118s and planet gears 116p . 118p the planetary gear sets 116 . 118 causes the sun gears 116s . 118s have a same rotational speed and the planet carrier 116c . 118c also have a same rotational speed. The wave 122 / 122 ' at the planet carrier 116c and at the sun wheel 118s for rotating at a reduced angular velocity with respect to the input ring gear 118r is accordingly rotated at a reduced angular velocity and thus gives an understeer ratio (its exact ratio by the respective configuration of the planetary gear sets 116 and 118 can be determined, for. B. Size / toothing of each of the sun gears 116s and 118s , Ring gears 116r and 118r and planet gears 116p . 118p ) between the ring gear 118r and the wave 122 / 122 ' ,

In contrast, when operating the brake clutch 126 (and release the brake clutch 124 , causing a rotation of the ring gear 116r enabled) of the planet carrier 118c and the sun wheel 116s each prevented from turning. Accordingly, the electric machine rotates 106 the ring gear 118r , and the rotating planet gears 118p (whose centers are through the planet carrier 118c be held stationary) turn the sun gear 118s , In addition, the sun wheel rotates 118s at a higher speed than the input ring gear 118r due to the increased angular velocity of the sun gear 118s in relation to the ring gear 118r while the planet carrier 118c is kept stationary. Accordingly, the operation of the brake coupling generates 126 an oversteer ratio (its exact ratio by the particular configuration of the planetary gear set 118 can be determined, for. B. Size / toothing of each of the interposed sun gears 118s , Ring gears 118r and planet gears 118p ) from the input ring gear 118r to the sun wheel 118s ,

The rotary coupling 128 is in 2 as selectively connecting the ring gear 116r with the planet carrier 118c illustrates a uniform transmission ratio of the input ring gear 118r to the wave 122 or 122 ' to accomplish. However, it should be understood that the rotary clutch 128 can be used to identify any two independent nodes of the four in the lever diagram 2 to generate a uniform transmission ratio from the input ring gear 118r to the wave 122 or 122 ' creating, whereby the same constructive purpose is achieved by the connection of the ring gear 116r with the planet carrier 118c through the rotary coupling 128 will be shown.

With a view to 3 , which is a simplified lever diagram of the powertrain 100 are exemplary operating modes of the vehicle powertrain 100 explained in more detail. As mentioned above, the vehicle drive train 100 the engine 102 and one or both electrical machines 104 . 106 selectively use to the final drive unit 130 To supply driving power and generate electrical energy that can be stored in one or more vehicle batteries (not shown). As in 3 represented represents the planetary gear set 114 generally an output for the final drive 130 over his ring gear 114r available, with the inputs from the electric machine 104 on her sun wheel 114s and the internal combustion engine 102 on his planet carrier 114c be recorded. In addition, the output of the electric machine 106 over the manual transmission 132 on the ring gear 114r recorded for a synchronized rotation with the shaft 122 / 122 ' (not in 3 shown) and / or the final drive unit 130 is secured.

In an electric vehicle mode, the input brake can 112 be actuated, causing a rotation of the shaft 120 (please refer 1A-1C) and the planet carrier 114c is prevented. Accordingly, the vehicle may pass through one or both of the electrical machines 104 . 106 are driven. In one example is the electric machine 106 a primary electric machine with respect to the powertrain 100 , the primary or exclusive driving force for the final drive unit 130 provides. Because the rotation of the shaft 122 / 122 ' (please refer 1A-1C) also the ring gear 114r turns, turns the sun gear 114s rotated, creating a rotary input for the electric machine 104 is provided, whereby the electric machine 104 generate electrical energy for storage in a vehicle battery. Alternatively, the electric machine 104 the driving force for the drive unit 130 (simultaneously with the electric machine 106 also the driving force for the final drive unit 130 ) over the sun wheel 114s provide.

The motor 102 can be used to connect to the final drive unit 130 supplied power can be used, for. B. when the battery power of the electric machine (s) 104 and / or 106 is relatively low. Accordingly, the input brake 112 be solved, so the engine 102 the driving force of the planet carrier 114c feeds and thereby the rotational force to the ring gear 114r outputs. One or both of the electrical machines 104 or 106 can be used to generate electrical energy to recharge the vehicle battery (s) by turning inputs through the manual transmission 132 receive. In addition, that of the ring gear 114r received rotary input on the above-described different transmission ratios are modified, whereby a division between the power of the engine 102 allows the to the final drive unit 130 and to the electric machine 106 is sent to change them.

The exemplary powertrain 100 allows the flexible use of an electrical machine, eg. B. an electric machine 106 , via a manual transmission 132 comprising a plurality of planetary gear sets. In particular, the manual transmission with at least the oversteer and understeer ratios enables a relatively narrow operating speed range of the electric machine 106 that can be used flexibly to provide motive power to the vehicle wheel or wheels or to generate electrical power from the drive motion over a broader range of vehicle speeds.

It should be understood that the foregoing is a description of one or more embodiments of the invention. The invention is not limited to the particular embodiment (s) disclosed herein, but is defined solely by the following claims. Furthermore, the statements made in the foregoing description refer to particular embodiments and are not to be construed as limitations on the scope of the invention or the definition of the terms used in the claims except where a term or phrase has been expressly defined above. Various other embodiments and various changes and modifications to the designated embodiment (s) will be apparent to those skilled in the art. All of these other embodiments, changes, and modifications should be understood to be within the scope of the appended claims.

As used in this specification and claims, the terms "for example", "for example", "as" and "equal" and the verbs "comprise", "comprise", "contain" and their other verb forms when used with each view as being open to a listing of one or more components or other items, which means that the listing is not to be understood as excluding other, additional components or items. Other terms are to be interpreted in their broadest reasonable sense, unless they are used in a context that requires a different interpretation.

Claims (10)

A hybrid powertrain for a vehicle, comprising: a co-drive manipulator having a first input adapted to be driven by an internal combustion engine and a second input configured to be driven by a first electric machine; and a selective amplifier including first and second planetary gear sets, each of the first and second planetary gear sets having a rotating component mounted on a rotatable shaft driven by the co-drive manipulator such that a rotating input provided on the second planetary gear set second electric machine which selectively drives the rotatable shaft at a plurality of gear ratios including at least one speed-reducing gear ratio and a speed-increasing gear ratio. Hybrid powertrain after Claim 1 wherein the selective amplifier further comprises: a rotary clutch configured to selectively secure a first ring gear of the first planetary gear set to a second planet gear carrier of the second planetary gear set for rotation therewith; and a first brake clutch configured to selectively limit the rotation of the first ring gear. Hybrid powertrain after Claim 2 and further comprising a second brake clutch configured to selectively limit rotation of the second planet carrier. Hybrid powertrain after Claim 1 , Further comprising a brake clutch, which is designed to limit the rotation of a sun gear of the first planetary gear set and a planet carrier of the second planetary gear set. Hybrid powertrain after Claim 1 wherein the first planetary gear set includes a first sun gear fixed to a second planet carrier of the second planetary gear set for rotation therewith. Hybrid powertrain after Claim 1 wherein the rotating component of the first planetary gear set is a first planet carrier of the first planetary gear set and the rotating component of the second planetary gear set is a second sun gear of the second planetary gear set. Hybrid powertrain after Claim 1 wherein the co-drive manipulator includes a third planetary gear set. Hybrid powertrain after Claim 7 wherein the first input is a third planet carrier of the third planetary gear set, the second input is a third sun gear of the third planetary gear set and the rotatable shaft is driven by a third ring gear of the third planetary gear set. Hybrid powertrain after Claim 1 wherein the selective amplifier further comprises: a rotary clutch configured to selectively secure a first ring gear of the first planetary gear set to a second planet gear carrier of the second planetary gear set for rotation therewith; a first brake clutch configured to selectively limit rotation of the first ring gear with respect to a stationary housing; and a second brake clutch configured to selectively limit rotation of the second planetary carrier with respect to the stationary housing. Hybrid vehicle, comprising: an internal combustion engine; a variety of electrical machines; a co-drive manipulator having a first input configured to be driven by an internal combustion engine and a second input configured to be driven by a first one of the plurality of electrical machines; and a selective amplifier including first and second planetary gear sets, each of the first and second planetary gear sets having a rotating component mounted for rotation with a rotatable shaft driven by the co-drive manipulator such that a rotating input connected to the second planetary gear set is received by a second one of the plurality of electric machines, selectively drives the rotatable shaft at a plurality of gear ratios including at least one speed-reducing gear ratio and a speed-increasing gear ratio.

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